Hydraulic equalizer



Nov. 1l, 1952 LE ROY M. DAv|s 2,617,555

HYDRAULIC EQUALIZER Filed Sept. 29, 1948 3 Sheets-Sheet l Nov. 1l, 1952 LE ROY M. DAvls 2,617,555

HYDRAULIC EQUALIZEIR Filed Sept. 29, 1948 5 Sheets-Sheet 2 1NVENToR.

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Nov. 11, 1952 ROY M. DAvls HYDRAULIC EQUALIZER 3 Sheets-Sheet I5 Filed Sept. 29. 1948 Patented Nev. 11, 1952 UNITED STATES PATENT OFFICE HYDRAULIC EQUALIZER Le Roy M. Davis, Glen Ellyn, Ill. Applieatiop september 29, 194s, serial No. 51,836

'z claims. (c1. 22o-85) My invention relates, generally, to hydraulic equalizers,v and it has particular relation to devices for neutralizing the unbalanced static force acting on a container holding fluid, such as the water box of a steam condenser, due to openings in the container walls for inlet and discharge pipes. V

This unbalanced force is equal to the product of the unit pressure at the opening in the container and the area of the opening. Where the pressure is relatively low, or where the area of the opening is relatively small, or when container is lrigidly supported, this force maybe neglected.

However, this force may become -a factor which must be taken into consideration in certain instances. For example, in the majority of cases where a steam condenser is employed in conjunction with a steam turbine, the condenser is not rigidly supported by its foundation, but is Welded or bolted to the turbine exhaust flange with only a portion of its weight being transmitted by coil springs to the condenser foundation; the remaining weight going to the turbine foundation by means of the turbine housing. Due to temperature changes the condenser, being rigidly supported from above, moves in a vertical direction an'appreciable amount, thus making it necessary to provide expansion joints inthe cooling water intake and outlet pipes. Since the expansion joints are incapable of transmitting force, the unbalanced force due to the pipe opening in the condensers water box will result in a moment acting on the turbine housing which, in turn, may cause distortion adversely affecting operation of themoving parts of the machine, or if extreme, result in a mechanical failure of the turbine.Y The diameter of the cooling water intake or outlet may be of the order of from forty to fifty inches. The water may be circulated through the condenser at a pressure as high as seventy pounds per square inch. Thus the force involved may be of the order of from 88,000 to 137,500 pounds in `these particular circumstances. q

The force actsv in one direction or the other depending upon whether the pressure within the container is above or below atmospheric pressure; Thus, if the container is operating under a vacuum, the force acts oppositely to that in which it acts if the pressure within it is above atmospheric pressure.

It has been proposed to counteract this unbalanced force on the condenser by introducing an equal force acting in the opposite direction and whose reaction acts against a fixed support, such as a pier or wall of a building. Such an arrangement would be, in reality, a hydraulic jack with a piston area equal to the area of the opening in the condensers waterA box and with the unit pressure of the fluid in the jack equal to the unit pressure of the fluid in the' condensers Water box at the opening. This hydraulic jacking device must be placed diametrically opposite the opening in the condensers Water box and a i-lxed support must be provided to take the reaction. Such an arrangement has serious disadvantages since it mayl be'diicult, if not impossible, to provide the iixed support for taking the reaction. The cost of -a-'xed 'supe port to take forces of the magnitudel mentioned previously will be a big item of expense. VIn th'e conventional divided w-ater box it is impossible to place the hydraulic jacking device opposite the opening, since the two inlet pipes and the two outlet pipes are placed diametrically opposite one another. A

The object of my invention is to provide a self-contained hydraulic equalizer for a condenser or a like fluid container to automatically counteract an unbalancedstatic force resulting from an opening in the condensers water box, using the hydraulic jack principle, but ,directing the reaction so that it acts on the wall of the condenser rather than requiring a separate fixed support, the device being located 'at the bend in a pipe communicating with the condenser and having an expansion joint between the bend and the condenser so that the direct force of the hydraulic equalizer exactly balances the hydraulic force acting on the bend in a coaxial direction with the pipe and condenser pipe openingand further to apply the concepts of myinvention where the bend in ther pipeis or less or with a straight pipe having no bend therein. v

Other objects of my invention will, in part, be obvious and in part appear hereinafter.

My invention is disclosed in the embodiments thereof shown in the accompanying drawings, and it comprises the features of construction, combination of elements and arrangement of parts which will be exemplified in the constructions hereinafter set forth and the scope of the application of which will be indicated in the appended claims.

For a more complete understanding of the nature and scope of my invention, reference can behad tothe following detailed description,

3 taken together with the accompanying drawings, in which:

Figure 1 is a top plan view of a hydraulic equalizer constructed in accordance with my invention and illustrating how it may be connected to a condenser only a part of which is shown;

Figure 2 is a view, in front elevation, of the hydraulic equalizer shown in Figure 1, there being shown a hydraulic equalizer for both the inlet andi outlet pipes for the eender-riser;

Figure 3 is a View, somewhat diagrammatic in character, illustratinghow the chamber formed by the second expansion joint and the pressure plate can be connected directly to the container or condenser so that the pressure therein will be applied in the chamber rather than the re duced pressure existing in the pipe at the. bend Y fll designates. eener-ally, aY con,- ay be employed in; conjunction .e for reeeivne5,i c 'ne and earn exhausted therefroin.` In

curated through the condenser I0; For this purpose the condenser I0 is provided with intake openings Il and discharge openings I2 which may be located opposite each other as illustrated in Figure 2. The openings II and I.2- may have a `diameter of forty-eight inches and the pressure Within the condenser t0 at which the waterV is circulated therethrough may be of the order of seventy pounds per square.v inch. It will be un.- derstd that the particular sizes and pressures referred to; hereinare for illustrative purposes; @th-er types and sizes of condensers can be einployed.-with other ysizes of intake andV discharge openingsand otherpressures may be employed. Moreoyer,Y insteadrof, water, a gas may be. emplayed as the fluid in. the container Ill. In seine.. cases; the pressure may be below atmospheric, pressure at the discharge opening I2. However, Since the,l present invention has been applied successfully in conjunction with conf densers f or use. with steam turbines, the details of its applicationthereto will be set forth herein.

In the particular condenser I shown in Figure 2, it is'contemplated that the cooling waterv will be circulated through both of the intake openings I-Iv and! :out of the discharge openings I 2 at the same timeandl thatthe intake and discharge pressures will' be equal' on both sides of the., condenser. Accordingly, under these concrees; tendlng to, move the condenser need. and can. be disregarded... However.;itnlayy be the; case that it may be necessary te` mterniet the flew efeeeling water through one of the intake openings I lj and drain one side of the condenser I0, the water passages being separated byv closing valve It'. As a result, under these conditionsV the st aticforce. tending to move., the condenser Illwill be equali to the arithmetic sum of the pressures at the inlet and outlet openings times their respective areas. This force may be suicient in some cases to move the condenser IU sufciently to rupture the connection between it and the turbine or to distort the turbine housing causing operating difficulties, or to move it slightly from its foundations. It is to neutralize such a static force that the present invention is particularly addressed.

Iit, will be noted that short lengths of pipe I3 and I4 extend from the intake and discharge openings I I and I2 and that they terminate in flanges I3' and I4. Standard practice in the past hasbeen to provide expansion joints, shown generally at I5, between the short lengths of pipe I3; and` I4 and intake and discharge pipes I6 each of which has a ninety degree bend that is indicated, generally, at I'I in Figure 1. The intake. and discharge pipes I6 may be supported rigidly by a framework I8 and also by a wall IS through which they extend. The expansion joints. I5v permit. the condenser Ill tomove slightly without affecting the fixed location of. the rigidly held intake and discharge pipes I,6., Also the: expansion joints I5 prevent the application of the, forces just referred toV to, the pipes, I6-

It will be Observed that each of the expansion joints I5,k terminates in flanges 2l)Y which arev secured by suitable. means to flanges, 2 I. and 22 locatedrespectively at` theendsof short sectionsv of pipe` 2,3 and 24. and the intake andl discharge pipes I6,

As ill-usIaatedv in Figure., 1,.the. outside surface 25 of the bend I'I in the pipe I6 has applied thereto a strut. 2.5 inthe, form. of a eineA which. at. its other Tend,- bears against a blind flange 2.1. The.y blind flange, 2J bearsagainst a flange. 28 of, a second expansion joint 2,9 which corresponds4 in size. to, the, expansion. joint I 5. The expansion joint.; 2,9, also has aflange 2 3 at, its other end which bears against. a flange 30 that is located at the outer end of a short length of pipe BI. The. pipe 3l has, an internal diameter which is the. same as the internal diameter of the pipe I6.. Itsfouter end is lclosed by a pressureY plate 32. It will be understood that the area of the pres.- sure. plate, i2V within the short length, of pipe 3| is, equal to, the area of the intake or discharge opening Il or 2 in the container or condenser IIL Itis. noted h ere that a chamber, shown generally lat 33, is formed by the blind flange 21, expansion. joint 2.9., short llength of pipe 3l andthe pressure plate 32. The( chamber 3 3will be referred to hereinafter in. pointing out how my intention functions- Igt will be understood that the static pressure exerted" by the, water within the pipes. I5 also is applied to theinner surface of the bend II on the side opposite the surface 2.5. In order to permit the force o n bendII to. counterbalance the egual'V and opposite force acting 4on blind iiangeA 2T, the strut 26 is provided as described. In ad'ditiom reenforcing plates 3B- extend between Athe bendiAI'IY and theblind flangey 21 for the same purpose.

Withinv each of the pipe struts 26 therev is a conduit. 3l which extends from theV blindv flange 2`IA intoeach of thepipes I-S. It will be understood that eachA conduit 31 places the associated chainber 33 in communication Ywith the interior of the corresponding pipe I'Si and that the chamber` 33 is filled with iiuid, water in this particular case. 'I-he pressure exerted Within leach of the chambers 3 3 is thesame as, exists inthe corresponding pipe-I6; e

In some instances it may be found that. the pressure at bend I1 due to velocity. and friction losses is somewhat less than the pressure in the container I0. Where it is desired to have the same pressure within the chamber 33 that is present within the container I0, the conduit 38, Figure 3, can be employed. It will be observed that the conduit 38 extends from the chamber 33 into the container or condenser II). In most instances, the kinetic energy due to velocity of the uid in pipe I6 may be discounted as compared to the static forces within the condenser III due to static pressure. y y

From'what has been said it will be apparent that a force is exerted on the pressure plate 32 which is equal to the force that is exerted on the container or condenser I as a result of the static pressure released by the intake opening I I or discharge opening I2. It remains to show how this force applied to the pressure plate 32 is equalized in accordance with my invention.

For thisV purpose three or-more combination tension and compression members, shown generally at 39, may be provided. As shown in Figure 2, each of these members comprises a sleeve or pipe 40 which is adapted to resist compres-sion and a rod 4I extends therethrough that is threaded at both ends and is adapted to resist tensile stresses. Nuts 42 are threaded onto the ends of the rods 4I to hold them in position. As shown in the drawings th-e members 39 extend :between the pressure plate 32'and a ring 43. Each ring 43 is secured as by welding to the adjacent end of each short pipe Isection 23 and 24 and is secured as by bolts to the adjacentflanges I 3' and I4. Trapezoidal reinforcing plates 44`extend lbetweenvthe rings 43 and the flanges 2I at the other ends of the pipe sections 23 and 24. Instead of connecting the tension-compression members 39 to a separate ring 43, they may be connected directly to the shell of the condenser I9. However, where the present invention is added to a condenser piping system that has been installed previously with the expansion joints I5 in place, I have found that it is advantageous to employ the particular construction just described.

It will be apparent now that the force due to static pressure which acts on the condenser IU as a result of the presence of either of the openings II or I2 is automatically equalized .by the provision of the chamber 33 and the tensioncompression members 39 which serve to apply the force acting on the pressure plate 32 tothe container or condenser I9 either directly or through the agency of the ring 43 or its equivalent construction. Since the unbalancing effect of each of the openings II and I2 is automatically self-compensated, there is no resultant force tending to move the container or condenser I0.

In Figures 4 and 5 of the drawings, a modification of my invention is illustrated in which the bend II' in the pipe I6 is less than ninety degrees. Specifically, the bend I'I is at an angle of thirty-three degrees thirty minutes.

The outside surface 25 of the bend'I'I is engaged by one end of a `strut 26' Which, like that described hereinbefore, maybe in the form of a pipe. In addition, plates $3 may extend radially from the pipe 26', as shown more clearly in Figure 5, for the purpose of distributing the force more fully over the outside surface 25.

If desired a shut-off valve, shown generally at 49, may be provided between the ring 43'and the short length pipe I3. It will be understood, of course, that the valve 139 may be omitted. Also,

in both of the embodiments of the invention shown in Figures 1 and 2 and 4 and 5 a drain valve 50 may be provided in a suitable pipe which extends from a suitable aperture in the pressure plate 32. The valve 50 is provided, as will be understood readily, to permit the chamber 33 to be drained if desired.

In the embodiments of the invention which have been described, it will be understood that the same pressure is present within the chamber 33 that is present either in the pipes I6 or in the condenser I 0 depending upon the location of the conduit 3l or 38. At any event, it is desired that substantially the same pressure be applied within the chamber 33 that is present within the condenser IIl. This pressure within the chamber 33 reacts in one direction against the blind ange 2'I and through the strut 26 and plates 36 or the strut 26' and the plates 48 to equalize the pressure applied on the inside surface of the bend II or I'I. This lsame force also acts in the opposite direction against the pressure plate 32. By means of the tension-compression members 39, the force acting on the pressure plate 32 is transferred to the condenser I I) so that there is no net force reacting on it which would tend to effect its movement.

In Figure 6 of the drawings I have shown a construction for equalizing the force Votherwise applied to a condenser I Where the intake pipe I6 does not have a bend close to the container Ill. but rather there is a substantial length of straight runl or" the pipe. The showing here is somewhat diagrammatic. It will be observed that a collar 52 is fastened onto the pipe I6 beyond the expansion joint I5.' Struts 53ex' tending angularly from the pipes l and collar 52 serve Ato react against the same and against blind flanges 2'I of a: pair of expansion joints 29 which are interposed between the blind anges 2'I and a pair of pressure plates 32. This provides two chambers 33 within which the pressure is maintained through conduits 3l to be equal to the pressure within the pipes I6 or within the container I3. The construction is such that the sum of the areas of the pressure plates 32 to which the fluid pressure is applied is equal to the area of the opening II in the container I0 and the eiective center of action of the hydraulic forces acting on pressure plates 32, as if such forces were resolved to a single force, lies on the central axis'of opening II. The sets of tension-compression members 39, preferably three in each set, serve to interconnect each ofthe pressure plates 32 with the condenser I0.

Since certain further changes can be made in the foregoing constructions and different embodiments of the invention can be made without departing from the spirit and scope thereof, it is intended that all matter shown in the accompanying drawings and described hereinbefore shall be interpreted as illustrative and not in a limiting sense.

' condenser, opposite and parallel to said opening therein; an expansible pressure chamber disposed between said plates, a pressure transmitting conduit interconnecting said pressure chamber and the interior of said condenser, and a plurality of tension compression members connecting one of said pressure plates and said condenser whereby the static hydraulic forces within said condenser may be balanced by the static forces acting on said one pressure plate.

2. For attachment to a condenser carrying pressurized fluid wherein an opening has been formed for the reception of suitable piping thereby creating an unbalanced static force within said condenser, a hydraulic equalizer comprising in combination, an inlet pipe received in said opening formed in said condenser, one end thereof being rigidly secured to said condenser and the other end thereof rigidly secured at a point remote from said condenser; a transversely disposed expansion joint in said pipe, a pair of pressure plates disposed in `spaced parallel relation opposite said opening in said condenser exteriorly of said pipe and condenser, an expansible pressure chamber disposed between and communicating with said two plates, rigid connecting members between the exterior of said pipe and one of said plates, rigid tension compression members connecting the second of said plates with said condenser, and a pressure transmitting conduit communicating between the interior of said pipe and said pressure chamber, whereby the static hydraulic pressure within said condenser may be transmitted along said pipe and conduit to said pressure chamber so that the force thereby exerted on said pressure plate connected with said condenser may oppose the unbalanced static force exerted within said condenser.

3. For use with a condenser containing fluid under pressure and in which an opening is formed resulting in the application of an unbalanced static force to said condenser tending to move the same, a hydraulic equalizer comprising in combination, a pipe receivable in said opening and having an expansion joint interposed therein, a pressure plate positioned exteriorly of said pipe and said condenser, strut means bearing, at one end, against said pipe beyond said expansion joint therein and at the opposite end against a blind flange member, a second expansion joint interposed between said pressure plate and said blind flange member and forming a iiuid tight chamber therewith, conduit means communicating between said chamber and said condenser to transmit the static pressure within the latter to said chamber and said pressure plate, and retaining tension rod and compression sleeve means connecting said plate to said condenser in a manner to transmit force exerted on said plate from said pressure plate to said condenser whereby said unbalanced static force in the latter is neutralized.

4. The invention, as set forth in claim 3, wherein said pressure plate is opposite and parallel to said opening in said condenser and said retaining rod and sleeve means extend at right angles to and between said pressure plate and said condenser.

5. For use with a condenser holding a body of pressurized iiuid and in which an opening is formed resulting in the application of an unbalanced static force to said condenser, the combination comprising, a pipe member, having an expansible joint and a bend portion interposed therein, communicating with said condenser via said opening therein; a pressure plate positioned exteriorly of said pipe and condenser, strut means bearing at one end against the exterior surface of said 'pipe at said bend therein, the interior lsurface of said bend having said unbalanced force applied thereto, a blind ange member mounted at the other end of said strut means, a second expansion joint interposed between said iiange and said pressure plate and connected therebetween to provide a fluid tight chamber therewith, conduit means communicating with said chamber and said pipe for transmitting iiuid pressure within said pipe to said chamber whereby said unbalanced force -on said bend is counterbalanced by force exerted on said flange by said fluid pressure and transmitted to said pipe bend via said strut means, and retaining rod and sleeve means rigidly connecting said plate to said condenser for transmitting to said condenser force exerted on said plate by said iiuid pressure for neutralizing said unbalanced static force thereon.

6. For use with a condenser holding a fluid under pressure and in which an opening is formed resulting in the application of an unbalanced static force to said condenser, a hydraulic equalizer comprising in combination, a straight pipe received at one end in said opening in said condenser and anchored rigidly at its opposite end, a collar member rigidly mounted about said pipe, an expansion joint interposed in said pipe intermediate said collar member and said opening, at least two pressure plates positioned symmetrically on opposite sides of said pipe exteriorly of said condenser, at least two strut means mounted at one end to and disposed angularly outward from said collar, a blind flange member mounted at the opposite end of each of said strut means, parallel to and spaced from one of said plates, expansion joint means interconnecting each of lsaid ange members with one of said plates toform two fluid tight chambers, conduit means communicating with said chambers and the interior of said pipe for transmitting fluid pressure within the latter to said chambers, and rigid tension and compression retaining members interconnecting said pressure plates with said condenser whereby said unbalanced static force within the latter is neutralized by the forces exerted on said plates.

7. The structure as set forth in claim 6, wherein the sum of the effective areas of said pressure plates acted upon by said fluid pressure is equal to the area of said opening in said condenser and the eiective center of action of the hydraulic forces exerted on said pressure plates lies on the central axis of said opening.

LE ROY M. DAVIS.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 45,849 Mowbray Jan. 10, 1865 123,169 Grimshaw, Jan. 30, 1872 777,632 Henry Dec. 13, 1904 942,666 Romstaedt Dec. 7, 1909 1,320,520 Allen Nov. 4, 1919 1,496,910 Smith June 10, 1924 1,778,657 Aoki Oct. 14, 1930 1,990,189 King Feb. 5, 1935 FOREIGN PATENTS Number Country Date 528,964 Germany July 6, 1931 

